Rotary engine

ABSTRACT

A rotary engine comprising a first group of piston-cylinder elements secured to a first case segment and a second group of piston-cylinder elements secured to a second case segment. The case segments are movably secured together and rotate on sleeves which rotate about a fixed shaft. Each piston of the first group reciprocates in a cylinder of the second group while the case segments rotate about and drive the sleeves. Each case segment is drivingly connected to a planetary gear and moves the planetary gear around a fixed sun gear such that the planetary gear secured to power transmission discs, drivingly connected to the drive shaft of the engine, causes the drive shaft to rotate. Connector links between case segments and the planetary gears are connected to provide a mechanically advantage such that movement of a piston and cylinder in opposite directions relative to each other causes the planetary gear, to which each link is eccentrically connected at diagonally opposed positions, to be moved around the fixed sun gear.

United States Patent 11 1 [111 3,739,755 Folstadt 1 June 19, 1973 ROTARY ENGINE [76] Inventor: Robert H. Folstadt, 639 Treasure, Examlrfer caflton Cmylc Garland 75040 Assistant Examiner-Michael Koczo, Jr.

Attorney-Howard E. Moore and Gerald G. Crutsinger [22] Filed: Nov. 13, 1970 [21] Appl. No.. 89,184 ABSTRACT 52 us. c1. 123 43 B, l23/8.47, 123/47 R, A fotary engine comprising a first group of Piswm 48/36 cylmder elements secured to a first case segment and 51 1111. C1. F02b 57/00 a Sewn! t of pism-cylinder elements Secured to 58 Field of Search 123/847, 8.45, 8.09, a Second segment The case Segments are movably 123/8277 43 A, 43 3,43 C, 43 AL4344, 74 secured together and rotate on sleeves which rotate R 74 A, 18 A, 47 418/34, 35, 36 about a fixed shaft. Each piston of the first group reciprocates in a cylinder of the second group while the case [56] References Cited segments roltate abltout and dricille the sleeves. Each casg se ment is rlvlng y connecte to a anetary gear an UNITED STATES PATENTS mt wes the planetary gear around a t xed sun gearsuch 1,733,965 10/1929 Howard 123/74 A that the planetary gear secured to power transmission 3,288,122 11/1966 Atsalos et a1. 418/34 X discs, drivingly connected to the drive Shaft of the em i zg fi y i: gine, causes the drive shaft to rotate. Connector links 2899945 M959 igg'; 123/43 B between case segments and the planetary gears are 4/1942 Ndsonnmu 123/347 connected to provide a mechanically advantage such 1,250,859 12/1917 Grimmett 23 347 that movement of a piston and cylinder in opposite dil,596,375 8/1926 Riesenecker 123/8.47 rections relative to each other causes the planetary 1,695,888 923 Dowdey 3/8- gear, to which each link is eccentrically connected at 9 4/1933 y l23/8-47 diagonally opposed positions, to be moved around the 2,362,550 11/1944 Hansen 123/8.47 fixed sun gear FOREIGN PATENTS OR APPLICATIONS 1,227,382 3/1960 France l. 123 s.47 9 Clams 16 Drawmg Flglms I56 60/ Y m 9 11 log 32 M 1,, r /65 9a 1112125 9 n2 3 31$ 54 2a i Patented June 19, 1973 3,739,755

8 Sheets-Sheet 1 mws R. Robert H. F0 0'! ATTOR/VE Patented June 19, 1973 3,739,755

8 Sheets-Sheet 4 /50 /20 /22 4 I36 ma [6 INVENTOR..

Robe/f H. Fosiadf A rro rs Patented June 19, 1973 3,739,755

8 Sheets-Sheet 5 1 m /20 a //46 Ma MmM" f in INVENTOR. Robert H. Fo/sfadf ATTOR/VE 3 Patented June 19, 1973 8 Sheets-Sheet 6 w 5 mm N 7 5 R mm 0 W .2 W 1 A Patented June 19, 1973 3,739,755

8 Sheets-Sheet '7 INVENTOR. Robert H. Fo/slaa'f BY f h I i e TURN S Patented June 19, 1973 I 3,739,755

8 Sheets-Sheet 8 mvzmozz. Robert H. Fo/s/adf ROTARY ENGINE BACKGROUND OF INVENTION An engine is generally defined a device for transforming energy, especially heat energy, into a useable form of mechanical work. Power originates in a cylinder-piston unit and is transferred through suitable power transmission means, generally comprising a connecting rod rotatably mounted on a crank shaft, to a drive shaft.

Brake engine efficiency, the ratio of the brake horsepower to the ideal horsepower, of internal combustion engines heretofore developed has been undesirably low because of mechanical friction losses, failure to convert potential energy of all moving parts of the engine into a useable form of power, and leakage adjacent cylinder walls.

SUMMARY OF INVENTION v a preferred embodiment, operates on a two-stroke cycle so that more power can be obtained for a given piston displacement volume,'and to minimize mechanical losses which would accompany operating valve mechanism. However, I contemplate slight modification to provide other cycles of operation and other means for providing pressure in cylinders.

Two groups of piston-cylinder elements are provided, each group of cylinder-piston elements moving as a unit to minimize pivotal connections thereby minimizing mechanical friction losses and weight of members transmitting power from the groups of piston-cylinder elements to the drive shaft of the engine.

A primary object of the invention is to provide an engine having high efficiency.

Another object of the invention is to provide an engine having a low weight per horsepower developed.

A further object of the invention is to provide an engine having cylinders which move through an unrestricted atmosphere for cooling same.

A further object of the invention is to provide an engine having improved power transmitting means between piston-cylinder elements and a drive shaft.

A still further object 'of the invention is to provide an engine having a minimum number of moving parts to minimize wear of component parts thereof.

Other objects of the invention will become apparent upon referring to the detailed description hereinafter following and to the drawings annexed hereto.

DESCRIPTION OF DRAWING Drawings of two embodiments of the invention are annexed hereto so that the invention may be better and more fully understood, in which:

FIG. 1 is a cross-sectional view taken substantially along line I-I of FIG. II;

FIG. 11 is a cross-sectional view taken substantially along line 11-" of FIG. I;

FIG. IIIis a cross-sectional view taken substantially along line III-III of FIG. II;

FIG. IV is a cross-sectional view taken substantially along line IVIV of FIG. III;

FIG. V is a cross-sectional view similar to FIG. III with the piston-cylinder elements moved to a position they would occupy at the beginning of a power stroke;

FIG. VI is a cross-section view similar to FIG. V with the piston-cylinder elements moved to the position which they would occupy at the beginning of the next power stroke;

FIG. VII is wiring diagram of the ignition system;

FIGS. VIII-XV are diagramatic views illustrating positions occupied by the connection links as the pistoncylinder elements move through a cycle of operation; and

FIG. XVI is a fragmentary cross-sectional view similar to FIG. V of a modified form of the invention.

Numeral references are employed to designate like parts throughout the various figures of the drawing.

DESCRIPTION OF A PREFERRED EMBODIMENT The preferred form of the invention, illustrated in FIGS. I-XV of the drawing, is a six cylinder, two-stroke cycle, rotary, spark ignition engine using a fuel-air mixture and pre-compression within the cylinder behind the piston. The preferred form of the invention has intake and exhaust ports in the cylinders.

A modified form of the invention is illustrated in FIG.

XVI of the drawing. The primary difference between the first and second embodiments is that the second embodiment has inlet and exhaust valves as will be hereinafter more fully explained.

Referring to FIG. I of the drawing, numerals 1-6 generally designate piston-cylinder elements of the engine generally designated by numeral 10.

As best illustrated in FIGS. I-III, engine 10 is supported by shaft 12 having opposite ends extending through openings in upwardly extending portions 14 and 16 of engine mount 18. Suitable means is provided to prevent rotation of shaft 12, such as keys 20 and 21. A sun gear 22 is secured to shaft 12 by suitable means, such as key 24, for preventing relative movement between gear 22 and shaft 12.

A hollow tubular sleeve 26 is rotatably secured around a segment of shaft 12, and suitable anti-friction means, such as needle bearings 28 and 30, is disposed between the outer surface of shaft 12 and the inner surface of sleeve 26 allowing the sleeve to rotate freely on said shaft.

A fly wheel 32 is secured to an outer portion of sleeve 26 and is urged into engagement with shoulder 34 on said sleeve by a lock nut 36 threadedly secured to the end of sleeve 26. Suitable lock means, such as key 38 is provided to cause fly wheel 32 and sleeve 26 to rotate as a single unit. The fly wheel 32 acts as an introrevolution governor by absorbing excess energy delivered by pistons during the early portion of the power stroke and releasing this energy during the latter portion of the stroke when the piston is delivering reduced power.

A flange 40 extends outwardly from the inner end of sleeve 26, and is secured by a suitable connectors 42 to a disc 44. Disc 44 has an opening 46 through a central portion thereof through which a central portion of shaft 12 extends.

A gear 48 is secured to sleeve 26 adjacent fly wheel 32, and is rigidly connected to said sleeve by suitable means such as key 50. Gear 48 is disposed in meshing relation with a gear 52 which is rigidly connected to drive shaft 54 by key 56.

Drive shaft 54 is rotatably secured in bearings 57 and 59 supported by upwardly extending portion 16 of engine mount 18.

A second hollow tubular sleeve 58 is telescopically disposed adjacent the other end of shaft 12 and rotates freely about said shaft on anti-friction means, such as needle bearings 60. Sleeve 58 has an outwardly extending flange 62 on the inner end thereof, and is secured by suitable connectors 63 to disc 64 having an opening 66 extending through a central portion thereof throughwhich shaft 12 rotatably extends.

It should be noted that discs 44 and 64 are rotatably disposed on shaft 12 adjacent opposite sides of gear 22 which is rigidly secured to shaft 12. A seal member 68 extends circumferentially around discs 44 and 64 and has opposite edges secured thereto as best illustrated in FIGS. II-IV of the drawing forming a closure which may be partially filled with oil for lubrication of gear 22 and planetary gears 70 and 72.

Referring to FIGS. II and III of the drawing, planetary gears 70 and 72 are secured to shafts 74 and 76, respectively, by set screws 78 and 80. Shaft 74 and shaft 76 are rotatably secured in spaced apertures in discs 44 and 64, and the planetary gears are rotatable with shafts 74 and 76. The planetary gears 70 and 72 are in meshing relation with sun gear 22 such that rotation of shafts 74 and 76 cause planetary gears 70 and 72 to move around sun gear 22, imparting rotation to discs 44 and 64 and consequently causing sleeves 26 and 58 to rotate about fixed shaft 12. The discs 44 and 64 are support means for planetary gears 70 and 72, and it should be appreciated that other support means could be employed.

As best illustrated in FIG. III, rollers 82 and 84 are rotatably secured to pins 86 and 88 which have opposite ends secured in spaced apertures in discs 44 and 64. Rollers 82 and 84 are positioned in rolling engagement with the inner surface of seal member 68 for maintaining planetary gears 70 and 72 in proper alignment, and in meshing relation with sun gear 22.

As best illustrated in FIGS. II and VI, shaft 74 has crank plates 90 and 92 fixedly secured to opposite ends thereof. Crank plate 90 has a pin 94 secured thereto upon which one end of link 96 is pivotally secured. The other end of link 96 is pivotally secured to case segment 100 by a connector 97.

Crank plate 92 has a pin 95 secured thereto about which one end of link 98 is pivotally secured. The other end of link 98 is pivotally secured to case segment 102 by a connector 99.

Shaft 76 to which planetary gear 72 is secured has crank plates 90 and 92' secured to opposite ends thereof, having pins 94 and 95' pivotally connected to ends of links 96 and 98. Links 94 and 95 have ends pivotally secured by connectors 97 and 99, respectively, to case segments 100 and 102.

As best illustrated in FIGS. I, II and IV pistoncylinder elements 1, 3 and are positioned about the periphery of a first case segment generally designated by numeral 100; and piston-cylinder elements 2, 4, and 6 are positioned about the periphery of a second case segment generally designated by numeral 102.

Referring to FIGS. II and IV of the drawing it should be noted that case segment and case segment 102 are of identical construction, and preferably castings of alloy metal. Suitable fillets 104 are provided on case segment 100 to strengthen the connection between piston-cylinder elements 1, 3 and 5 and the case segment 100, and also to provide fuel passages as will be hereinafter more fully explained. It should be noted that fillets 106 on case segment 102 are identical to fillets 104 on case segment 100.

Case segment 100 and case segment 102 supporting piston-cylinder elements 106, have openings through a central portion thereof about which bosses 108 and 110 having bearings 112 and 114, respectively, are mounted to cause case segments 100 and 102 to rotate freely about sleeves 26 and 58.

Referring to FIG. III of the drawing, each of the piston-cylinder elements 1-6 has a piston 120, secured by a curved piston rod 122 to the front wall 124 of a cylinder 126. The cylinder 126 is connected by a fillet 104 or 106 to a case segment 100 or 102.

The inner walls 128 of cylinders 126 and the outer surface 130 of pistons are curved. As illustrated in FIG. II, a transverse cross-section through cylinders 126 and pistons 120 is circular. As best illustrated in FIG. III, a longitudinally cross-section through cylinders 126 and pistons I20 reveals that the longitudinally curvature of the inner wall 128 is concentric with the central axis of shaft 12. The inner surface of front wall 124 and back wall lie in planes extending radially from the central axis of shaft 12.

The front face 120a and rear face 1201) of each piston 120 also lie in planes extending radially from the central axis of shaft 12.

It is to be noted that each piston 120 has suitable sealing means such as rings 132 to prevent leakage between the inner wall 128 of each cylinder 126 and the outer surface of each cylinder 120.

It should be appreciated that cylinders 126 may be segmented to facilitate assembly and positioning cylinders 120 therein. Each backwall 125 of each cylinder 126 has an opening formed therein through which a piston rod 122 slidably extends. Suitable means, not illustrated, is employed for sealing about piston rod 122 to prevent leakage of fluid through the opening in the backwall 125.

As best illustrated in FIGS. IV and V, means is provided for delivering a fuel air mixture'into the inside of each cylinder 126. Intake ports 134 are formed in the wall of cylinder 126 and communicate with by-pass passage 136 formed in the cylinder wall. A fuel passage having a first section 138, communicating with by-pass passage 136, and a second section 140, communicating with the inside of case sections 100 and 102, has a valve 142 disposed therein. The valve 142 is preferably spring loaded to allow flow of fluid therethrough when pressure inside cylinder 126 behind piston 120 is less than pressure inside case segments 100 and 102.

By-pass passage 136 connects intake ports 134 with injection ports 144 formed in cylinder 126 intermediate opposite ends thereof.

An exhaust port 146 extends through the wall of each cylinder 126 through which products of combustion are removed from the forward portion of the cylinder. As best illustrated in FIG. III, exhaust ports 146 are positioned slightly forwardly of injection ports 144 such that as piston 120 moves toward backwall 125, the exhaust port 146 is uncovered by the piston and consequently opened before injection ports 144 are opened.

Each cylinder 126 has suitable means for igniting a fuel-air mixture. Spark plugs 148 of piston-cylinder elements 2, 4 and 6 are connected through spark plug wires 156 to a wiper ring 151 on case segment 102. Spark plugs 148 on piston-cylinder elements 1, 3, and 5 are connected through spark plug wires 152 to a wiper ring 153 on case segment 100. As best illustrated in FIG. II, insulating material 151a and 153a is employed to electrically insulate wiper rings 151 and 153 from the case segments 100 and 102.

Brushes 154 and 155, mounted on supports 14a and 16a, respectively, are resiliently urged into contact with wiper rings 151 and 153.

Referring to FIGS. II and VII of the drawing, brush 154 is connected through conductor 156 to contacts 156a, 156b, and 1156c in distributor cap 158. Brush 155 is connected through conductor 157 to contacts 157a, 157b, and 1570 in distributor cap 158. Distributor 160 has a rotor 161 rotatably by shaft 162 driven by timing gears 163 and 164. Timing gear 164 is secured to drive shaft 54.

Shaft 162 has a cam 165 secured thereto for opening and closing breaker points 166 which are connected through conductors 167 and 168 to a conventional ignition coil.

Suitable spark advance mechanism such as spring diagram device 170 is employed for advancing contacts relative to the cam. A vacuum line 172 is connected between the spark advance mechanism and carburetor 175.

As best illustrated in FIG. II, carburetor 175 is secured to motor mount 18 and is connected through fuel line 176 to a source of fuel. The quantity of fuel is regulated through a suitable throttle control linkage 177. Carburetor 175 supplies a fuel-air mixture to passage 178 formed in shaft 12. Passage 178 communicates through opening 179 with angular chamber 180 formed in the inner end of sleeve 58 which in turn communicates through openings 181 with the inside of case segments 101) and 102.

As best illustrated in FIG. II of the drawing, case segments 100 and 102 are rotatably secured together by bearings 182 which seal space therebetween.

OPERATION Fuel is delivered from carburetor 175 through passage 178, opening 179 angular chamber 180 and opening 181 to the inside of case segments 100 and 102. Referring to FIG. IV, the fuel-air mixture passes through passages 140, valve 142, passage 138, by-pass passage 136, and intake points 134 to the inside of cylinder 126 behind piston 120. As piston 120 moves toward backwall 125 of cylinder 126, the fuel-air mixture is compressed until injection ports 144 are opened to deliver the fuel-air mixture to the forward portion of the inside of cylinder 126.

On the compression stroke a fuel-air mixture in the forward portion of the cylinder is compressed until a spark is provided by spark plugs 148 resulting in combustion of the fuel-air mixture causing an increase in pressure in the forward portion of the cylinder.

As the piston and cylinder move in opposite directions relative to each other, the exhaust port 146 becomes uncovered. Since the pressure in the cylinder is higher than that of the atmosphere, some of the prodnets of combustion flow out of the cylinder through the exhaust port. Continued movement of the piston uncovers injection ports 144 allowing compressed air-fuel mixture behind piston 120 to flow through intake ports 134, by-pass passage 136, and injection ports 144 allowing air-fuel mixture to rush into the forward portion of the cylinder to evacuate products of combustion therefrom.

The movement of the piston back toward the forward portion of the cylinder creates a partial vacuum in the rear portion of the cylinder causing fuel to flow through valve 142 behind the piston. After the fuel-air mixture has been compressed in the forward portion of the cylinder, the spark plug ignites the charge to begin the power stroke.

The cycle hereinbefore described is accomplished in two strokes of the piston, or in one revolution of plane tary gear shafts 74 and 76.

Referring to FIGS. VIII-XV of the drawing, connector link 96, pivotally secured to case segment 100, and connector link 98, pivotally connected to case segment 102, impart rotation to planetary gear 70.

The connector links 96 and 98 are illustrated in FIGS. VIII and IX of the drawing in the position which they occupy relative to planetary gear when pistons 120 of piston-cylinder elements 1, 3, and 5 are positioned in cylinders 126 of piston-cylinder elements 6, 2, and 4, respectively, as illustrated in FIG. VI of the drawing at the beginning of combustion and expansion portion of the cycle. The increase in pressure in the forward portion of cylinders 126 of piston-cylinder elements 2, 4, and 6 urges case segment 100 in a clockwise direction as viewed in FIGS. VI, VIII and IX while simultaneously urging case segment 102 in a counter clockwise direction. Movement of case segment 100 and case segment 102 in opposite directions causes connector links 96 and 98 to move to the positions illustrated in FIGS. X and XI at which time the piston cylinder elements 1-6 are positioned substantially as illustrated in FIG. III. Continued movement of the case segments cause links 96 and 98 to be positioned as illustrated in FIGS. XII and XIII of the drawing at which time piston-cylinder elements 1-6 are positioned as illustrated in FIG. V of the drawing.

Ignition of the fuel air-mixture in cylinders 126 of piston-cylinder elements 1, 3 and 5 causes connector links 96 and 98 to move from the positions illustrated in FIGS. XII and XIII to the positions illustrated in FIGS. XIV and XV.

It should be noted that links 96 and 98 are positioned relative to planetary gear 70 such that pin 94 connected through a case segment to the face 1200 of the piston-cylinder element upon which pressure of combustion is exerted travels through the outer portion of the orbital path while pin connected to the cylinder in which pressure is exerted travels through the inner portion of the orbital path. Thus, it should be apparent that because of the positioning of pins 94 and 95 force resulting from therecoil action of cylinder elements acts through a shorter radius measured from the center of shaft 12 than does the force exerted by the piston engaged in the power stroke. Thus, the torque exerted on discs 44 and 64 by the recoil of cylinders is less than the torque in the opposite direction transferred thereto by the pistons.

It should also be apparent that the pin 94, as viewed in FIG. X, exerts force on a portion of gear 70 which is a greater radial distance from the centers of shaft 12 and gear 22 than force exerted by pin 95, as viewed in FIG. XI. Gear 70 tends to yield to force exerted through pin 94 while said gear tends to resist movement by force exerted through pin 95 in positions illustrated in FIGS. X and XI because of the differences in the distances between the pitch circles of gears 22 and 70 and the points relative to gear 70 at which the forces are applied.

Links 96 and 98 pivotally secured to planetary gear 70 translate oscillatory motion of case segments 100 and 102 to circular motion to roll gear 70 around gear 22 causing discs 44 and 64 to rotate about shaft 12. Piston-cylinder elements 1-6 move in a circular path with discs 44 and 64 while oscillating relative thereto circumferentially about shaft 12.

SECOND EMBODIMENT A modified form of the invention is illustrated in FIG. XVI of the drawing wherein exhaust ports and injection ports in the cylinder walls have been eliminated.

In the form of the invention illustrated in FIG. XVI, fuel air mixture is delivered through intake ports 134 as hereinbefore described.

Face 120a of piston 120' has a valve seat 200 formed therein through which intake valve 202 is slidably disposed. Intake valve spring 204, disposed between shoulder 206 in a central bore through piston 120' and retainer 208 secured to stem 210 of said valve, urges valve 202 toward seat 200. An actuating pin 212 is secured to valve stem 210 and positioned to engage a cam surface 214 on backwall 125 of the cylinder.

It should be appreciated that as piston 120 moves toward backwall 125 the fuel-air mixture is compressed behind piston 120. As actuating pin 212 engages cam surface 214 valve 202 is moved to the position illustrated in FIG. XVI allowing the compressed fuel-air mixture behind piston 120 to flow'through passage 205 into the forward portion of the cylinder.

Piston rod 122' has a hollow portion in which an exhaust valve stem 220 having an actuating pin 222 movable in a slot 224 is slidably disposed. Valve member 226 on stem 220 is urged toward valve seat 228 by a spring 230.

Actuating pin 222 engages the outer surface of backwall 125 to urge exhaust valve 226 to the open position allowing products of combustion to escape around valve stem 220 and through passage 232 to the atmosphere.

From the foregoing, it should be readily apparent that I have developed an internal combustion engine having cylinders which recoil relative to pistons slidably disposed therein during the power stroke wherein both the piston and the cylinder imparts rotation through connector links and planetary gears to an output shaft. Movement of all parts of the engine result in production of useful work rendering greater efficiency than had been heretofore realized in internal combustion engines.

It should be readily apparent that by minor modification the embodiments of the invention hereinbefore described may be converted to employ other types of fuel or to run as a steam engine without departing from the basic concept of my invention.

Having described my invention I claim:

1. A prime mover comprising, a support means; a fixed shaft secured to the support means; a sun gear fixed on the shaft; first and second discs rotatable about said fixed shaft on opposite sides of the sun gear; at least one axle rotatably secured to outer portions of said first and second discs; a planetary gear on said axle, said planetary gear being positioned in meshing relation with the sun gear; first and second crank means secured to said axle, said crank means extending in opposite directions from said axle; first and second links pivotally connected to said first and second crank means; a cylinder secured to said first link; a piston slidably disposed in the cylinder, said piston being secured to said second link, thereby causing said piston and cylinder to rotate about said fixed shaft; means to cause the piston and cylinder to reciprocate; and power output means operably connected to the discs.

2. The combination called for in claim 1 wherein the power output means comprises a hollow tubular member rotatably secured about the fixed shaft; and means to secure the hollow tubular member to at least one of the discs.

3. A prime mover comprising, a central shaft; a plurality of piston-cylinder elements; a first case segment rotatable about said central shaft secured to a first half of the piston-cylinder elements; a second case segment rotatable about said central shaft secured to the second half of the piston-cylinder elements; means to rotatably secure the case segments together to position pistons of the first half of the piston-cylinder elements in cylinders of the second half of the piston-cylinder elements and pistons of the second half of the piston-cylinder elements in cylinders of the first half of the pistoncylinder elements; means to selectively introduce pressurized fluid into the cylinders to cause the pistons to reciprocate in the cylinders thereby causing the first and second case segments to oscillate relative to each other; a first link secured to the first case segment; a second link secured to the second case segment; a sun gear fixedly secured to said central shaft; a disc rotatably secured to said central shaft; a planetary gear disposed in meshing relation with said sun gear; a crank shaft secured to said planetary gear and rotatably supported by said disc; first and second cranks on said .crank shaft secured to said first and second links; and

power output means secured to said disc.

4. In a two cycle internal combustion engine, a cylinder having a forward end and a back end; closure means across each end of the cylinder, the closure means across the back end of the cylinder having an opening formed therein; a piston slidably disposed in the cylinder, said piston dividing the cylinder into a forward portion and a back portion; a rod on the piston extending through the opening in the closure across the back end of the cylinder; means for sealing between edges of the opening and the rod; means for delivering fuel to the back portion of the cylinder such that fuel is compressed behind the cylinder as the cylinder moves toward the closure across the back end of the cylinder; means to transfer the compressed fuel from the back portion of the cylinder to the forward portion thereof to evacuate products of combustion from the forward portion of the cylinder; means to initiate combustion in the forward portion of the cylinder to urge the piston toward the back end of the cylinder; power output means; first power transmission means connected to said rod and to said power output means; and second power transmission means secured to said cylinder and to said power output means, said first and second power transmission means being adapted to permit simultaneous movement of the piston and the cylinder in opposite directions.

5. The combination called for in claim 4 with the addition of a second piston secured to the forward end of the cylinder, and a second cylinder secured to the back end of the piston forming a plurality of piston-cylinder elements, each of said piston-cylinder elements having a longitudinal axis which is semi-circular; a fixed shaft;

and wherein said first and second power transmission means comprises; means rotatably secured relative to said fixed shaft to support the piston-cylinder elements for movement circumferentially about said shaft; and means to translate arcuate reciprocating motion of the pistons and cylinders to circular motion.

6. In a prime mover, a mounting shaft; first and second piston-cylinder elements, each of said elements comprising a cylinder having inner and outer closure means at opposite ends thereof, a piston rod having an inner end secured to the inner closure means of the cylinder, a piston on the outer end of the piston rod, the outer closure means of the cylinder having an aperture therethrough, the piston rod of each of the pistoncylinder elements being slidably disposed in the aperture of the other piston cylinder element; first and second support means secured to the respective pistoncylinder elements; means to rotatably secure each of said support means to the mounting shaft; a sleeve on said mounting shaft; and power transmission means to drivingly connect the first and second support means to the sleeve.

7. in a device of the class described, a toothed surface, a gear in meshing relation with said toothed surface, said gear being rotatably secured to support means which is rotatable about a central axis; a piston; a first link connected between the piston and the gear; a cylinder; a second link connected between the cylinder and the gear; means to secure said first and second links to diametrically opposed portions of the gear; means to reciprocate the piston relative to the cylinder to cause the gear to rotate moving the support means relative to the toothed surface; a drive shaft; and means between the drive shaft and the support means to rotate the drive shaft.

8. The combination called for in claim 2 wherein the means to cause the piston and cylinder to rotate about the fixed shaft is rotatably secured to the hollow tubular member.

9. In a prime mover, a mounting shaft; first and second piston-cylinder elements, each of said elements comprising a cylinder having inner and outer closure means at opposite'ends thereof, each of said inner closure means having exhaust openings extending therethrough, exhaust valves disposed in each of said openings and arranged to be opened as an inner closure means on a first element moves toward an outer closure means on a second element; a piston rod having an inner end secured to the inner closure means of the cylinder; a piston on the outer end of the piston rod, said piston being positioned in said cylinder such that the piston rod extends through an aperture formed in the outer closure means, each of said piston having intake passages formed therein; intake valves disposed in said intake passages and arranged to be opened as a piston on a first element moves toward an outer closure means on a second element permitting flow of compressed fuel through the piston; first and second support means secured to the respective piston-cylinder elements; means to rotatably secure each of said support means to the mounting shaft; a sleeve on said mounting shaft; and power transmission means to drivingly connect the first and second support means to the sleeve. 

1. A prime mover comprising, a support means; a fixed shaft secured to the support means; a sun gear fixed on the shaft; first and second discs rotatable about said fixed shaft on opposite sides of the sun gear; at least one axle rotatably secured to outer portions of said first and second discs; a planetary gear on said axle, said planetary gear being positioned in meshing relation with the sun gear; first and second crank means secured to said axle, said crank means extending in opposite directions from said axle; first and second links pivotally connected to said first and second crank means; a cylinder secured to said first link; a piston slidably disposed in the cylinder, said piston being secured to said second link, thereby causing said piston and cylinder to rotate about said fixed shaft; means to cause the piston and cylinder to reciprocate; and power output means operably connected to the discs.
 2. The combination called for in claim 1 wherein the power output means comprises a hollow tubular member rotatably secured about the fixed shaft; and means to secure the hollow tubular member to at least one of the discs.
 3. A prime mover comprising, a central shaft; a plurality of piston-cylinder elements; a first case segment rotatable about said central shaft secured to a first half of the piston-cylinder elements; a second case segment rotatable about said central shaft secured to the second half of the piston-cylinder elements; means to rotatably secure the case segments together to position pistons of the first half of the piston-cylinder elements in cylinders of the second half of the piston-cylinder elements and pistons of the second half of the piston-cylinder elements in cylinders of the first half of the piston-cylinder elements; means to selectively introduce pressurized fluid into the cylinders to cause the pistons to reciprocate in the cylinders thereby causing the first and second case segments to oscillate relative to each other; a first link secured to the first case segment; a second link secured to the second case segment; a sun gear fixedly secured to said central shaft; a disc rotatably secured to said central shaft; a planetary gear disposed in meshing relation with said sun gear; a crank shaft secured to said planetary gear and rotatably supported by said disc; first and second cranks on said crank shaft secured to said first and second links; and power output means secured to said disc.
 4. In a two cycle internal combustion engine, a cylinder having a forward end and a back end; closure means across each end of the cylinder, the closure means across the back end of the cylinder having an opening formed therein; a piston slidably disposed in the cylinder, said piston dividing the cylinder into a forward portion and a back portion; a rod on the piston extending through the opening in the closure across the back end of the cylinder; means for sEaling between edges of the opening and the rod; means for delivering fuel to the back portion of the cylinder such that fuel is compressed behind the cylinder as the cylinder moves toward the closure across the back end of the cylinder; means to transfer the compressed fuel from the back portion of the cylinder to the forward portion thereof to evacuate products of combustion from the forward portion of the cylinder; means to initiate combustion in the forward portion of the cylinder to urge the piston toward the back end of the cylinder; power output means; first power transmission means connected to said rod and to said power output means; and second power transmission means secured to said cylinder and to said power output means, said first and second power transmission means being adapted to permit simultaneous movement of the piston and the cylinder in opposite directions.
 5. The combination called for in claim 4 with the addition of a second piston secured to the forward end of the cylinder, and a second cylinder secured to the back end of the piston forming a plurality of piston-cylinder elements, each of said piston-cylinder elements having a longitudinal axis which is semi-circular; a fixed shaft; and wherein said first and second power transmission means comprises; means rotatably secured relative to said fixed shaft to support the piston-cylinder elements for movement circumferentially about said shaft; and means to translate arcuate reciprocating motion of the pistons and cylinders to circular motion.
 6. In a prime mover, a mounting shaft; first and second piston-cylinder elements, each of said elements comprising a cylinder having inner and outer closure means at opposite ends thereof, a piston rod having an inner end secured to the inner closure means of the cylinder, a piston on the outer end of the piston rod, the outer closure means of the cylinder having an aperture therethrough, the piston rod of each of the piston-cylinder elements being slidably disposed in the aperture of the other piston cylinder element; first and second support means secured to the respective piston-cylinder elements; means to rotatably secure each of said support means to the mounting shaft; a sleeve on said mounting shaft; and power transmission means to drivingly connect the first and second support means to the sleeve.
 7. In a device of the class described, a toothed surface, a gear in meshing relation with said toothed surface, said gear being rotatably secured to support means which is rotatable about a central axis; a piston; a first link connected between the piston and the gear; a cylinder; a second link connected between the cylinder and the gear; means to secure said first and second links to diametrically opposed portions of the gear; means to reciprocate the piston relative to the cylinder to cause the gear to rotate moving the support means relative to the toothed surface; a drive shaft; and means between the drive shaft and the support means to rotate the drive shaft.
 8. The combination called for in claim 2 wherein the means to cause the piston and cylinder to rotate about the fixed shaft is rotatably secured to the hollow tubular member.
 9. In a prime mover, a mounting shaft; first and second piston-cylinder elements, each of said elements comprising a cylinder having inner and outer closure means at opposite ends thereof, each of said inner closure means having exhaust openings extending therethrough, exhaust valves disposed in each of said openings and arranged to be opened as an inner closure means on a first element moves toward an outer closure means on a second element; a piston rod having an inner end secured to the inner closure means of the cylinder; a piston on the outer end of the piston rod, said piston being positioned in said cylinder such that the piston rod extends through an aperture formed in the outer closure means, each of said piston having intake passages formed therein; intake valves disposed in said intake passages and arranged to be opened as a piston on a first element moves toward an outer closure means on a second element permitting flow of compressed fuel through the piston; first and second support means secured to the respective piston-cylinder elements; means to rotatably secure each of said support means to the mounting shaft; a sleeve on said mounting shaft; and power transmission means to drivingly connect the first and second support means to the sleeve. 